Head suspension assembly having improved frequency response, accurate head positioning and minimized flying variation

ABSTRACT

A load beam is joined by its proximal end to a rigid actuator arm. The load beam has stiffening flanges projecting from its longitudinal edges. The flanges have a Z-axis measurement or height of at most about 0.4 mm. The flanges terminate co-extensive with the load beam surface. The distal end of the load beam has a load bearing dimple with a Z-axis height of at least about 0.10 mm. The flexure is attached to a distal end of the load beam. The load beam distal end may be narrower than the flexure. Longitudinal load beam edges in the base plate region may have a rail or tabs for supporting head connection. The load beam spring region may have a central area of reduced thickness. The load beam may have alignment and assembly tooling features. The flexure and the actuator base plate may be welded to the load beam, or the mounting arm and the load beam may be a unitary one-piece structure. Each flange may have a U-shaped or V-shaped cross-sectional profile, or each flange may taper from a minimum depth at a load beam proximal end to a maximum depth at a load beam distal end. The flexure may have areas of reduced thickness on the flexure arms.

FIELD OF THE INVENTION

This invention relates to an improved head suspension assembly (HSA) foruse in dynamic storage devices or rigid disk drives. More particularly,the present invention provides specific improvements to the constructionand assembly of the various components of an HSA to provide a suspensionof intermediate length with decreased pitch and roll stillnesses, inorder to decrease sensitivity of the HSA to fly height and driveassembly tolerances.

BACKGROUND OF THE INVENTION

In a magnetic rigid disk storage device, a rotating disk is employed tostore information in small magnetized domains located on the disksurface. By providing advanced mechanisms to accurately and rapidlyrecord/retrieve data to/from these domains, a large quantity ofinformation can conveniently be manipulated in a small physical volume.

Rigid disk storage devices typically include a frame to provideattachment points and orientation for other components, and a spindlemotor mounted to the frame for rotating the disk. A magnetic read/writehead capable of flying in close proximity to the rigid disk(s) enablesthe creation of the magnetic domains on the disk. The head is supportedand properly oriented in relationship to the disk by a head suspensionassembly which provides forces and compliances necessary for propertransducer operation. The suspension assembly and head are driven andpositioned with respect to the disk by an actuator mounted to the frame.

A typical head suspension assembly (HSA) includes an elongated loadbeam, an actuator plate attached to a proximal end of the load beam formounting the load beam to an actuator arm of a disk drive, and agimballing flexure at a distal end of the load beam. A head slider ismounted to the flexure and thereby supported in read/write orientationwith respect to an associated disk. Rails or flanges extend generallylongitudinally along the load beam to add rigidity and provide routingfor wire leads extending from the head slider. Commonly assigned U.S.Pat. No. 5,198,945, MAGNETIC HEAD SUSPENSION, issued Mar. 30, 1993,describes load beam transitional side rails or flanges, which graduallyprogress from a minimum Z-axis depth (that is, minimum height) at aproximal end of the load beam (adjacent to the rigid arm) to a maximumZ-axis depth (that is, maximum height) at a load beam distal end toprovide increased loading clearance and increased disk to suspensionclearance to facilitate lifting of the proximal end of the load beam.

On the load beam, between the distal end of the actuator plate and theproximal end of the rails or flanges, is an area of flexibility referredto as the spring region. Manufacturers and designers of such magneticdisk drives are continually looking for ways to increase storagecapacity while maintaining specific form factors (i.e., component sizesand dimensional relationships) for disk drive design. Improved resonanceperformance of the suspension, through higher resonant frequencies andlower gains for off track modes, allows for the utilization of a highernumber of data tracks per centimeter on the disk. A higher areal densityand more data storage per disk surface can thereby be obtained.

The general design of an HSA flexure allows the head to pitch about afirst axis, generally oriented longitudinally with respect to thesuspension, and roll about a second or transverse axis, perpendicular tothe first axis, when imperfections in the disk drive assembly tend toplace the head in improper positions relative to the surface of thedisk.

Also described in U.S. Pat. No. 5,198,945 are tooling features on theload beam, such as at the proximal end of the load beam or just proximalof a distal end of the load beam, to facilitate accurate angularplacement in alignment and assembly of the suspension.

A specific prior HSA, available from the assignee of the presentinvention and designated the Type 16, is designed for use with a 50%slider. The Type 16 requires that the Z-axis tolerance be held to+/-0.12 mm. However, there is a continuing need for improvements in HSAswhich would allow increased Z-axis tolerance.

Although certain features of the present invention are separately foundin conventional HSAs, the particular combination of features of the HSAsof the present disclosure has not previously been suggested to beassociated in a single HSA, and the present combination offers specificunobvious and improved advantages in performance that are not obtainablewith currently available HSAs.

SUMMARY OF THE INVENTION

In a head suspension assembly for attachment to a rigid actuator arm,the head suspension comprises in combination a spring load beam elementand a gimballing flexure having the following structural features.

The load beam is joined by its proximal end to the rigid actuator arm.The load beam has stiffening flanges projecting from longitudinal loadbeam edges. The flanges have a positive depth with a maximum Z-axisdepth measurement or height of at most about 0.4 mm from the load beamsurface. The flanges terminate co-extensive on the Z-axis with the loadbeam surface. The distal end of load beam element has a load bearingdimple. The dimple has a minimum Z-axis height of at least about 0.10 mmfrom the surface of the load beam to which a flexure means is attached.The flexure means is provided at a distal end of the load beam element.

Additional features which can be incorporated into the HSAs of thisinvention are as follows. The load beam may have one or more aperturesto allow ultraviolet curing of an epoxy adhesive bonding the read/writehead to the flexure. The width of the load beam distal end may be lessthan the width of the flexure to allow visibility of and access to themagnetic read/write head bonded to the flexure. The narrowness of theload beam distal end relative to the flexure also facilitates headbonding, location, inspection and measurement, and facilitatesvisibility of and access to interconnection means from the head.

Longitudinal load beam edges in the base plate region may have a meansfor supporting read-write head connection means, such as a longitudinalrail or supporting tabs. The load beam spring region may have a centralarea of reduced thickness. The load beam may have tooling features, suchas at the proximal end of the load beam or just proximal of a distal endof the load beam, to facilitate accurate angular placement in alignmentand assembly of the suspension.

In order to provide a greater dimple height, the dimple is formed in theload beam, rather than in the flexure, as has previously beenconventional. The load beam is formed of thicker sheet material than theflexure, thus allowing the formation of a higher dimple.

The flexure and the actuator base plate may be welded to the load beam.Alternatively, the actuator base plate may be eliminated, and themounting arm and the load beam may together be a unitary one-piecestructure etched out of the same sheet of material.

Each flange may have a U-shaped or V-shaped cross-sectional profile, oreach flange may be of a transitional depth having a minimum depth at aload beam proximal end and a maximum depth at a load beam distal end.

The flexure may have areas of reduced thickness, for example, on theflexure flexible arms.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 is a perspective view of a head suspension assembly according tothe teachings of the present invention.

FIG. 1A is a perspective view of a flexure of FIG. 1.

FIG. 2 is a perspective view of another head suspension assembly alsoaccording to the teachings of the present invention.

FIG. 2A ia a perspective view of a flexure of FIG. 2.

FIG. 3 is a partial perspective view of a head suspension assembly,similar to that shown in FIG. 1, showing one of the flanges cut-away.

FIG. 3A shows a cross-sectional view, taken along the line A--A of FIG.3, of a flange having a U-shaped profile.

FIG. 4 is a partial perspective view of a head suspension assembly,similar to that shown in FIG. 2, showing an aperture in the distal endof the flexure.

FIG. 4A shows a cross-sectional view, taken along line A--A of FIG. 4,of a flange having a V-shaped profile.

FIG. 5 is a perspective view of a head suspension assembly, similar tothat shown in FIG. 1, showing transitional flanges, which taper from aminimum depth at a proximal end of the flanges to a maximum depth at adistal end of the flanges.

FIG. 5A shows a cross-sectional view, taken along line A--A of FIG. 5.

FIG. 5B shows a cross-sectional view, taken along line B--B of FIG. 5.

FIG. 6 is a perspective view of a head suspension assembly, similar tothe partial view shown in FIG. 3.

FIG. 7 is a perspective view of a head suspension assembly, similar tothat shown in FIGS. 3 and 6, positioned in read/write relationship to adisk.

DETAILED DESCRIPTION OF THE INVENTION

Referring now to the drawings, FIGS. 1 and 2 illustrate two embodimentsof a head suspension assembly 10, 10' formed in accordance with theteachings of this invention. The head suspension assemblies according tothis invention are generally of the type referred to as a Watroussuspension system, such as described in U.S. Pat. Nos. 3,931,641 and4,167,765. Reference is made to these two patents for a more detaileddiscussion of the structure and use of Watrous suspension systems anddisk drive systems generally.

Suspension 10, 10' is mounted on a rigid actuator arm of a magnetic diskdrive (not shown) using swaging boss 12, 12' which projects upwardlyfrom base plate 14, 14' positioned against lower planar surface of loadbeam 16, 16'. U.S. Pat. No. 5,172,286, issued Dec. 15, 1992 and entitledLOAD BEAM INTERLOCKING BOSS, describes a mounting assembly for attachinga head suspension assembly to a rigid actuator arm, and this assemblymay advantageously be used in mounting the present novel HSAs. Ifdesired, other base plate structures and methods of attachment can beutilized for securing the load beam 16, 16' to the rigid actuator armemploying any known suitable connecting means such as screws, welding,swaging or bonding.

As shown in FIGS. 1 and 2, a load bearing dimple 18, 18' is formed in adistal portion of the load beam 16, 16' for confronting the flexure 20,20'. According to the present invention, load beam 16, 16'is generallyformed from a sheet of stainless steel, preferably a 300 series alloy,having a nominal sheet thickness of between about 0.05 to 0.10 mm. Thisis significantly thicker than the sheet material used in the flexure 20,20', where the load bearing dimple is conventionally formed. The sheetmaterial from which the flexure 20, 20' is formed has a nominalthickness between about 0.025 and 0.050 mm. The thicker material allowsforming of higher height load bearing dimple 18, 18' in a distal portionof load beam 16, 16' than has previously been possible when the dimpleis formed in the flexure. The ability to provide a broader range ofdimple heights and higher dimple heights allows HSAs according to thepresent invention to be able to fit into a larger range of disk-to-diskspacings.

The width of the proximal end 24, 24' of load beam 16, 16', adjacent tothe rigid actuator arm, is approximately equal to the actuator armwidth. The proximal end 24, 24' of load beam 16, 16' as illustrated inFIGS. 1 and 2, is provided with a tooling feature to facilitate accurateangular placement in suspension alignment, that is, proximally extendingtabs 22, 22'. Load beam 16, 16' width then tapers to a second narrowerwidth at the load beam distal portion 26, 26', and then abruptly reducesto a nose end 28, 28' third narrowest constricted width of between about0.5 to about 1.25 mm. This narrowest nose end 28, 28' of load beam 16,16' allows increased visibility of and access to the attached flexure20, 20' and read/write head 30 to facilitate such procedures as bonding,location, inspection and measurement. Increased visibility of and accessto sides and distal end of the head 30 further allow for easier routingof interconnection means from the head 30, to be routed along the loadbeam 16, 16', preferably along perimeter flanges 32, 32' and alongsupport means 34, 34' provided at a proximal end 24, 24' of the loadbeam 16, 16' in the region of the base plate 14, 14'. In addition,increased head exposure provided by the constricted nose end 28, 28' ofthe load beam 16, 16' permits the head 30 to access tracks closer in tothe disk hub, thus decreasing the number of accessible tracks lost withprevious wider HSAs.

The portion of load beam 16, 16' adjacent to base plate 14, 14' referredto as the spring region 36, 36', is resilient, while the remaininglength of the load beam 16, 16' is substantially rigid. Resiliency ispreferably enhanced by having a central area 38, 38' in the springregion 36, 36' of reduced thickness. This central area 38, 38' ofreduced thickness reduces load beam spring rate. The central area 38,38' is an area of partial thickness(es) or an aperture through the loadbeam material.

The rigidity of the remaining length of load beam 16, 16' is enhanced bystiffening flanges or rails 32, 32' which project toward the side of theload beam 16, 16' to which the flexure 20, 20' and the read/write head30 are to be attached. The flanges 32, 32' are alternatively be formedto project away from the side of the load beam 16, 16' to which theread/write head 30 is to be bonded. The flanges 32, 32' for HSAs of thepresent invention have a positive depth with a maximum Z-axismeasurement or height of at most about 0.4 mm from a surface of the loadbeam 16, 16', and the flanges terminate co-extensive on a Z-axis withthe opposing surface of the load beam 16, 16'. This flange depth is muchless than in previously available HSAs, and increases the back-to-backsuspension distance to increase disk-to-head loading clearance. When theflanges 32 have capture tabs 40, as shown in FIG. 1, the flanges 32 areso formed that the tabs 40 terminate co-extensive on a Z-axis with theplanar surface of the load beam 16.

As shown in FIGS. 3 and 3A, the flanges 32" have a U-shapedcross-sectional profile and a maximum Z-axis depth measurement ormaximum height of from about 0.25 to about 0.37 mm. Such flanges aresuitable for supporting head interconnection means encased in protectivetubing, generally having an overall diameter of about 0.23 to 0.38 mm.The flange 32" closer to the disk hub is cut back, as shown in FIGS. 3and 6, to further permit the head 30 to access disk tracks closer in tothe disk hub. As shown in FIGS. 4 and 4A, the flanges 32" have aV-shaped cross-sectional profile and a maximum Z-axis measurement ormaximum height of about 0.20 to about 0.25 mm, suitable for supportingtubed or tubeless head interconnection means, generally having anoverall diameter of about 0.025 to 0.23 mm.

As illustrated in FIGS. 5, 5A, and 5B, the flanges 32"" are of atransitional depth, having a minimum Z-axis measurement or height at aproximal end thereof (adjacent the load beam proximal end) and having amaximum Z-axis measurement or maximum height at a distal end thereof.Commonly assigned U.S. Pat. No. 5,198,945, issued Mar. 30, 1993,entitled MAGNETIC HEAD SUSPENSION, describes such transitional siderails or flanges, which provide increased loading clearance andincreased disk to suspension clearance to facilitate lifting of theproximal end of the load beam. Such transitional flanges areadvantageously used with the HSAs of the present invention. Flanges ofeither a U-shaped or a V-shaped profile may be formed as transitionaldepth flanges.

FIG. 6 shows another variation of the embodiments illustrated generallyin FIGS. 1 and 1A. As has been described above, in FIG. 6, the distalend 26 of the flange 32 and an adjacent portion of the load beam 16 iscut away, to facilitate smaller head-to-hub distance. Alternatively, theflange opposite the disk 58 hub is cut away (as shown in FIG. 7) toallow increased clearance for lift and drive merge tooling 56. The lifttooling involves a series of ramps assembled to a common bar, so thatthe ramps can be wedged between the suspensions, when the suspensionshave been assembled to an E-block (or when separate arms have beenassembled into a stack). The purpose of wedging the ramps between thesuspensions is to separate the head/sliders, and prevent thehead/sliders from contacting each other during handling. The mergetooling is similar in concept, except that the merge tooling is used tokeep the head/sliders separated, while they are positioned between thedisks during the drive assembly process.

As shown in FIGS. 1, 1A, 2 and 2A and as discussed above, flexure 20,20' is affixed to constricted nose 28, 28' at the distal end of loadbeam element 16, 16'. Constricted nose 28, 28' as has been discussedbriefly, is provided with load bearing dimple 18, 18' and with aperture42, 42' for ultraviolet curing of an epoxy adhesive used to bond flexure20, 20' to load beam element 16, 16'.

Flexure 20, as best illustrated in FIG. 1A, includes central headmounting support means 51, to which a head is to be bonded and which isseparated from the body of flexure 20 by cut-outs forming flexible arms46. Central head mounting support means 51 is depressed from the levelof the body of flexure by form lines 53 and 55. Flexible arms 46connect, at the extreme distal end of flexure 20, to central headmounting support means 51. Flexure 20 has several through features 44formed along the length of flexible arms 46. Through features 44 areareas of either complete or partial reduction in the thickness of theflexible arms 46, and are stamped, punched, etched, photolithographed,laser cut or otherwise formed in the surface of arms 46. The position,size and orientation of these through features 44 are selected tosubstantially reduce pitch and roll stiffness without greatlysacrificing lateral stiffness. Convex feature 47 also contributes tolateral stiffness of the flexure. Lateral stiffness affects access timeand settling time when actuating the head from one disk track toanother. Features 44 are generally rectangular and optionally haveuniform spacing between them and optionally have similar dimensions.Typically, features 44 have dimensions ranging from 0.15 to 0.165 mm by0.15 to 0.51 mm and a typical separation distance of 0.1 mm. Partialthrough features only cut through about 1/2 of the sheet material, whichhas a typical range of thickness of between 0.025 and 0.050 mm. Throughfeatures other than rectangular or alternative sizes and spacings areused and provide similar or even improved performance. Tooling hole 48and tooling slot 50 cooperate with corresponding hole 48 and slot 50 onload beam 16 in aligning and connecting flexure 20 to load beam 16.

Flexure 20' as best illustrated in FIG. 2A, is shown provided withtooling hole 48' and tooling slot 50' to assist in location of flexure20' to load beam 16' and in assembly of the suspension. Flexure 20'includes central head mounting support means 51', to which a head is tobe bonded and which is separated from the body of flexure 20' bycut-outs forming flexible arms 46'. Central head mounting support means51' is depressed from the level of the body of flexure by form lines 53'and 55'. Flexible arms 46' connect, at the extreme distal end of flexure20', to central head mounting support means 51'. Each flexible arm 46',at the end thereof proximal to the rigid actuator arm has a widest widthtapering to a narrowest width adjacent the central head mounting supportmeans 51'. Convex feature 47' contributes to lateral stiffness of theflexure.

During manufacture and assembly of the suspension assembly according tothe present invention, load beam 16, 16' is positioned relative toflexure 20, 20' by using tooling hole 48 and tooling slot 50, which arealigned with corresponding features 48, 50 on the flexure 20, 20'.

Alternatively, in any of the HSAs of the present invention, the mountingarm and the load beam may together be a unitary one-piece structureetched from the same sheet of material, so that the need for a separateactuator base plate is eliminated.

Significantly lower flexure gimballing stiffness for the present HSAallows decreased fly height variation by reducing torque against the airbearing due to manufacturing angular disparities. HSAs of the presentinvention are able to exert higher loads through the dimple/flexureinterface onto the read/write head without affecting pitch and rollstiffness of the flexure. This is a completely unobvious result, sincein previously available HSAs increasing load has had an adverse effecton flexure stiffness.

HSAs of this invention also have a high suspension offset capability. Inprevious HSAs, the load bearing dimple has conventionally been formed inthe flexure. The height of the dimple has been limited by the thinnessof the sheet material from which the flexure is made. Since the loadbeam is formed of a thicker sheet material than that used in forming theflexure, a dimple of greater height can now be formed in the load beam,resulting in higher suspension offset heights. Thus, HSAs of the presentinvention are able to fit into a larger range of disk drives of varyinglow to high disk spacings. Disk spacings as low as about 1.6 mm can beaccommodated, and the present HSAs work most effectively in disk driveswith Z-axis height tolerances of +/-0.25 mm.

Although the HSAs of the present invention are primarily designed foruse in 50% slider disk drives, they can be formed with a high suspensionoffset height combined with a 50% slider. Thus, the combined Z-axisheight is equal to that of a 70% slider and suspension, and the HSA ofthe present invention can then be retrofitted into a drive thatpreviously used a 70% slider and suspension. The present HSAs arecompatible with most rigid disk drives of between about 30 to 90 mm.Generally, HSAs of the present invention have a medium length load beamof about 18.03 mm (measured from the center of the swage boss to thecenter of the load dimple), although load beam lengths of between about10.1 to about 30.5 mm can suitably be used.

HSAs prepared in accordance with the teachings of this invention meetthe performance requirements of 50% sliders, including improvedfrequency response, more accurate slider positioning and minimizedflying variation. In addition, the presently provided HSAs are able toaccommodate specific applications requiring the ability to withstand lowto moderate operating shock, where lateral stiffness is not a keyrequirement. The present HSAs demonstrate higher resonance frequenciesand minimal flying variation, while accommodating a wide range of Z-axisheights. The design of the present novel HSAs is especially suitable foruse in disk drives having minimal disk spacings, and can be compatiblewith rigid disk drives of various sizes.

It is to be understood that either a standard flexure 20' (such as shownin FIGS. 2, 2A and 4) or a laterally stiff flexure 20 (such as shown inFIGS. 1, 1A, 3, 5, 6 and 7) may be used with any of the load beams asdescribed herein. The standard flexure 20' (as illustrated in FIG. 4)and the laterally stiff flexure 20 (as illustrated in FIG. 3, 6 and 7)may be provided an aperture 52, 52' which may be used for ultravioletirradiation of adhesive bonding head 30 to flexure 20, 20'. The reverseflanges, as described previously, are able to allow for very tight diskspacing, and can be from about 0.2 to about 0.25 mm for V-profileflanges (such as shown in FIGS. 4 and 4A) and about 0.4 mm for U-profileflanges (such as shown in FIGS. 3 and 3A). Nominal loads can range fromabout 30 to about 70 mN, with a load tolerance of +/-3 mN. Static pitchand roll of the head bond area can be held to +/- 45 min. Typical springrate of the HSA, that is, load change of the head due to Z-heightchanges, is 18 N/m. The flexure has a pitch stiffness of between about1.5 to about 2.0 μN·m/deg, a roll stiffness of between about 2.0 toabout 2.5 μN·m/deg, and a lateral stiffness of between about 4.7 toabout 12.5 μN·m/deg.

The present HSAs have controlled first and second torsion amplitudes,which prevent unacceptable off-track error in a typical application.Sway mode is the first mode to cause off-track motion for rotaryactuation with a frequency typically above 8000 Hz. Using a basicramping configuration, an HSA of the present invention can be liftedvertically approximately 100,000 times beyond nominal Z-height with novisible cracks in the flexure, with lifting done at a tooling hole 5.33mm from flexure center an the head being lifted vertically 0.4 mm fromthe disk surface. An HSA of the present invention withstand half sineshocks of 500 G's for 3 msec in vertical and lateral directions.

What is claimed is:
 1. A head suspension assembly for attachment to arigid actuator arm and for supporting a read/write head, said headsuspension assembly comprising, in combination:a load beam having aproximal end, a distal end, a first surface, a second opposing surface,stiffening flanges projecting from longitudinal edges of the load beam,and a load bearing dimple at the distal end, the proximal end joined tothe rigid arm, the stiffening flanges having a maximum depth of about0.4 mm from the first surface, and the flanges terminating co-extensivewith the second opposing surface of the load beam, each flange taperingfrom a minimum depth at a proximal end thereof adjacent the load beamproximal end to the maximum depth at a distal end thereof, and thedimple having a minimum height of about 0.1 mm from the first surface;and a flexure means attached at the distal end of the first surface ofthe load beam and interfacing with the dimple.
 2. A head suspensionassembly according to claim 1, adapted and arranged to operably supportloads through a dimple/flexure interface onto the read/write headranging from about 30 mN to about 70 mN.
 3. A head suspension assemblyaccording to claim 1, wherein a width of the distal end of the load beamelement is less than a width of the flexure, thereby allowing gimballingof the flexure arms to be unobstructed by the load beam.
 4. A headsuspension assembly according to claim 1, wherein a portion of the loadbeam adjacent the proximal end of the load beam is provided with asupport means for read-write head connection means along a longitudinaledge of the load beam.
 5. A head suspension assembly according to claim4, wherein the support means is a longitudinal bracket.
 6. A headsuspension assembly according to claim 4, wherein the support means isone or more supporting tabs.
 7. A head suspension assembly according toclaim 1, wherein a spring region of the load beam element is providedwith an area of reduced thickness therein.
 8. A head suspension assemblyaccording to claim 1, wherein the load beam is provided with toolingfeatures to facilitate accurate angular placement in suspensionalignment, slider bonding alignment and alignment of the load beam tothe rigid arm.
 9. A head suspension assembly according to claim 8,wherein a tooling feature for alignment of the load beam to the rigidarm is one or more proximally extending tabs at a proximal end of theload beam.
 10. A head suspension assembly according to claim 8, whereina tooling feature for suspension alignment or slider bonding alignmentis one or more apertures in the load beam element.
 11. A head suspensionassembly according to claim 1, wherein the flexure and an actuator baseplate are each welded to the load beam.
 12. A head suspension assemblyaccording to claim 1, wherein each flange has a U-shaped cross-sectionalprofile and the maximum depth of from about 0.25 to about 0.37 mm.
 13. Ahead suspension assembly according to claim 1, wherein each flange has aV-shaped cross-sectional profile and the maximum depth of about 0.25 mm,suitable for supporting either tubed or tubeless read/write headinterconnection means.
 14. A head suspension assembly according to claim1, in which the flanges are provided with extending tabs to providefurther support to read/write interconnection means.
 15. A headsuspension assembly according to claim 1, wherein areas of reducedthickness are provided on the flexure.
 16. A head suspension assemblyaccording to claim 1, wherein a length of the load beam from a center ofan actuator boss to a center of the load dimple is between about 17.8 to18.3 mm.
 17. A head suspension assembly according to claim 1, whereinone flange terminates at a point proximal of the distal end of the loadbeam to facilitate a smaller head-to-hub distance or to allow increasedclearance for lift and drive merge tooling.
 18. A head suspensionassembly according to claim 17, wherein the flexure and an actuator baseplate are each attached to the load beam by weldment.
 19. A headsuspension assembly for attachment to a rigid arm, said head suspensionassembly comprising, in combination:a load beam having a proximal end, adistal end, stiffening flanges projecting from longitudinal edges of theload beam, a first surface, a second opposing surface, a spring regionadjacent the proximal end, the spring region having an area of reducedthickness, tooling features located adjacent the proximal end andlocated just proximal of the distal end, and a load beam dimple at thedistal end, the proximal end joined to the rigid arm, the flanges havinga maximum depth of about 0.4 mm from the first surface, the flangesterminating co-extensive with the second opposing surface, each flangehaving a depth of 0 at a proximal end thereof adjacent the load beamproximal end and the maximum depth at a distal end of each flange, thedimple having a minimum height of about 0.1 mm from the first surface,the distal end of the load beam having a width less than a width of theflexure attached thereto, the proximal end of the load having a supportmeans for supporting read/write head interconnection means along alongitudinal edge thereof; and the flexure means attached to the distalend of the first surface of the load beam and interfacing with thedimple.
 20. A head suspension assembly according to claim 19, whereinthe tooling feature in the proximal end of the load beam is a pair oftooling tabs.
 21. A head suspension assembly according to claim 19,wherein tooling features in the distal end of the load beam are toolingapertures.
 22. A head suspension assembly according to claim 19, whereineach flange has a U-shaped cross-sectional profile and a maximum depthof from about 0.25 to about 0.37 mm.
 23. A head suspension assemblyaccording to claim 19, wherein each flange has a V-shapedcross-sectional profile and a maximum depth of about 0.25 mm, suitablefor supporting either tubed or tubeless read/write head interconnectionmeans.
 24. A head suspension assembly according to claim 19, wherein aflange is cut back to facilitate a smaller head-to-hub distance or toallow increased clearance for lift and drive merge tooling.